US6579078B2 - Multi-stage centrifugal compressor driven by integral high speed motor - Google Patents

Multi-stage centrifugal compressor driven by integral high speed motor Download PDF

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Publication number
US6579078B2
US6579078B2 US10/128,136 US12813602A US6579078B2 US 6579078 B2 US6579078 B2 US 6579078B2 US 12813602 A US12813602 A US 12813602A US 6579078 B2 US6579078 B2 US 6579078B2
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United States
Prior art keywords
rotor
stator
gap
bearings
shaft
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Expired - Lifetime
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US10/128,136
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US20020192089A1 (en
Inventor
M. Raymond Hill
Milovan R. Grbic
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EARNEST PACIFIC Ltd
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Elliott Turbomachinery Co Inc
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Priority to US10/128,136 priority Critical patent/US6579078B2/en
Assigned to ELLIOTT TURBOMACHINERY CO., INC. reassignment ELLIOTT TURBOMACHINERY CO., INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GRBIC, MILOVAN R., HILL, M. RAYMOND
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Assigned to EARNEST PACIFIC LIMITED reassignment EARNEST PACIFIC LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ELLIOTT TURBOMACHINERY CO., INC.
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/27—Rotor cores with permanent magnets
    • H02K1/2706—Inner rotors
    • H02K1/272—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis
    • H02K1/274—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of two or more circumferentially positioned magnets
    • H02K1/2753—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of two or more circumferentially positioned magnets the rotor consisting of magnets or groups of magnets arranged with alternating polarity
    • H02K1/278—Surface mounted magnets; Inset magnets
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/85—Starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2205/00—Specific aspects not provided for in the other groups of this subclass relating to casings, enclosures, supports
    • H02K2205/12—Machines characterised by means for reducing windage losses or windage noise
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
    • H02K5/1672—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings radially supporting the rotary shaft at both ends of the rotor

Definitions

  • small low flow rate compressors (below 800 ICFM (200 HP)) with discharge pressures below 150 psig were either screw or reciprocating type compressors. These screw and reciprocating type compressors were driven by small, induction type low speed (1800 to 3600 rpm) motors. Centrifugal compressors required high rotating speeds, this dictated use of gears to increase the drive speed to higher rotor speeds (approximately 5 to 20 times the drive speed). Initially, small centrifugal compressors were less efficient at low flow rates, had higher mechanical losses, and were not economical due to the requirement for speed increasing gears and additional bearings. Because of these problems, centrifugal compressors were not feasible for the low flow rate market segment.
  • the purpose of this invention is to provide an improved small compact high speed motor integrally designed with compressor stages to directly drive the compressor to a desired high speed without the need of a speed increasing gear and additional bearings for the gears.
  • the present invention is directed to a multi-stage, such as a two-stage centrifugal compressor, driven directly by a high speed motor shaft that is integrally part of the rotor comprised of two impellers mounted directly on both ends of the motor shaft.
  • the motor shaft which is supported on hydrodynamic bearings lubricated with oil is rotated by a stator powered by a high frequency inverter that is controlled electronically with a system that interacts with the power conversion system and Hall sensors.
  • variable speed permanent magnet motor having electronically commutated stator coils surrounding a rotor carrying permanent magnets, wherein there is a gap between the coils and the rotor, said rotor having a magnetic steel rotor shaft rotatably supported at each end by pressurized oil lubricated hydrodynamic bearings, wherein the stator coils are comprised of a plurality of stator wires extending longitudinally along the stator and continuing around the ends of the stator to define end turns;
  • a pump for introducing cooled oil into the bearings for lubricating the bearings and for cooling the bearings, rotor and stator coils, said bearing configured so that oil exiting from the bearings splashes over the supported ends of the shaft and splashes over the end turns of the stator coils, and
  • the invention is also directed to a method of starting a multi-stage centrifugal compressor with an integral high-speed motor, wherein the motor has a stator and a rotor rotationally supported therein defining a gap therebetween and wherein the rotor is supported at each end by hydrodynamic oil bearings, wherein the method is comprised of the steps of:
  • variable speed permanent magnet motor having electronically commutated stator coils surrounding a rotor carrying permanent magnets, said rotor having a magnetic steel shaft rotatably supported by bearings,
  • the stator and inverter are water cooled utilizing finned heat exchangers.
  • the gap between the rotor and the stator is controlled by inducing cool air to the gap 50 that purges the area from contaminates such as oil.
  • the rotor shaft is cooled by bathing the ends adjacent to the magnets in cool oil.
  • An alternate or enhancement to the shaft cooling is utilizing an axial hole through the rotor from the second stage impeller to the first stage impeller. Cool air from the second stage inlet is then passed through the shaft taking heat away.
  • the motive force for the air flow is the differential pressure from the second stage inlet to the first stage inlet.
  • the rotor is constructed of four half moon shaped samarium cobalt magnets mounted on a square cross sectioned steel shaft and retained by means of a prestressed composite carbon graphite fiber winding.
  • FIG. 1 is a schematic drawing showing the electrical system for providing electrical power to the motor during the startup and running mode
  • FIG. 2 is an illustration of the rotor with two compression stages, air path and intercooler
  • FIG. 3 is a split stator construction drawing
  • FIG. 4 is a cross-sectional view of an assembly illustrating details of FIG. 3;
  • FIG. 5 is a rotor construction drawing
  • FIG. 5A is a section view taken along lines “ 5 A— 5 A” in FIG. 5;
  • FIG. 6 schematically illustrates a rectifier circuit for converting the AC input to a DC voltage
  • FIG. 7 schematically illustrates the inverter circuit compose of six IGBT switches used to communicate the current to the motor during the startup and running mode.
  • FIG. 8 illustrates a boost chopper circuit composed of two IGBT switches used to step-up voltage level on the DC bus.
  • FIG. 1 illustrates the relation between an electrical control system, including a system controller 1 and a compressor controller 2 , and a power conversion system, including a rectifier 4 , a boost 5 , an inverter 6 , and a motor 7 .
  • the electrical control system interacts with the power conversion system and Hall sensors 3 to provide motor startup as well as motor full speed conditions to accommodate the compressor load.
  • FIGS. 2, 3 and 4 illustrate the rotor compressor configuration and air flow path with interstage air cooling.
  • Atmospheric air enters, through a first stage inlet 21 , a first centrifugal compressor stage 27 which compresses the air and causes the air to be heated.
  • the air is cooled in a heat exchanger 31 before entering a second stage 26 through a second stage inlet 24 .
  • the heat exchanger utilizes cool water entering at 29 and exiting at 30 to exchange the heat from the air to the water.
  • the second stage 26 further compresses the air 25 to the desired pressure level.
  • Pressurized air is introduced from an external source by line 23 to the gap 50 between the rotor 28 and the stator 52 to prevent oil from the bearings 53 , 54 supporting the rotor 28 from entering the gap 50 when the rotor 28 is beginning to rotate at start-up.
  • the arrangement related to bearing 53 will be described with the understanding that the arrangement related to bearing 54 will be similar.
  • Air forced into the gap 50 may be used to control the atmosphere between the rotor 28 and the stator 52 to prevent the entry of oil within the gap 50 or purge oil that may already be in the gap 50 .
  • the pressurized air through line 23 should be discontinued. If pressurized air were to be supplied to the gap 50 at high rotational speeds, undesirable friction and heating of the rotor 28 and the stator 52 would occur.
  • An alternate shaft cooling arrangement (not shown) is supplying cool air from the second stage inlet 24 through a hole in the shaft of the rotor 28 to the first stage inlet 21 .
  • the motive force for the air is the differential pressure of the second stage inlet 24 which is higher than the pressure of the first stage inlet 21 .
  • This arrangement can also be used in conjunction with the oil cooling.
  • a synchronous permanent magnet motor 7 is used to drive the compressor stages 26 and 27 .
  • the motor 7 is comprised of the stator 52 and the rotor 28 .
  • the stator 52 is manufactured using electrical steel laminated disks 60 that are stacked together, as shown in FIG. 3 . Laminated material for the disks 60 (two shown) is of high quality thereby resulting in low losses.
  • This stack of the stator 52 contains three-phase distributed wye connected windings in twenty-four stator slots.
  • the stator 52 is split in the middle to accommodate a high temperature plastic spacer 8 , in place of one or more disks 60 , having spoke passageways 64 extending radially to supply pressurized air through line 23 from the stator 52 OD (outer diameter) to the gap 50 between the stator 52 ID (inner diameter) and the rotor 28 OD. This air is used to remove or to prevent from entering any oil in the gap 50 . Air is provided through line 23 into a passageway 66 extending through a water-cooled jacket 10 , which is around the disks 60 , to an annulus 70 extending around the outside of the stator 52 . From there the air is distributed through the spoke passageways 64 into the gap 50 .
  • Openings between the wires of the end turn 9 wires adjacent to the gap 50 are provided for oil drainage.
  • stator 52 On the outer periphery of stator 52 is mounted the water-cooled jacket 10 that provides cooling for the heat generated by the copper and iron losses created in the stator 52 . Therefore, cooling occurs by both the oil flow through the bearings 54 and flow of water through the jacket 10 .
  • the rotor as shown in FIGS. 5 and 5A, has permanent magnets 12 made of rare earth samarium cobalt. There are four poles per rotor.
  • the magnet geometry is a half moon shape to minimize magnet end losses and minimize stress levels.
  • the half moon shaped magnets 72 a - 72 d are mounted on a square cross sectioned steel shaft 75 which is used to complete the conductive field.
  • the magnets are encased axially with non-conductive titanium end caps 13 . Titanium allows sensing of the rotor magnets stray fields by Hall sensors without shorting the magnets.
  • the rotor magnets are retained radially to the shaft with a prestressed composite winding 14 .
  • This composite winding 14 is a high strength, low electric conductivity and high resistance carbon graphite fiber composition. The prestressed condition of the composite fiber winding prevents magnet lift-off from the shaft which could damage the magnets during operation.
  • the input voltage to the power stage can vary from 380 V to 575 V, 50 or 60 Hz.
  • the AC input voltage is converted by the half controlled rectifier circuit to a DC voltage whose levels can be changed by the boost phase.
  • the DC voltage is changed to an AC voltage with desired magnitude and frequency by the inverter stage.
  • the stator windings are connected to the inverter output.
  • the three phase, half-controlled thyristor shown in FIG. 6 is used to convert the input voltage to a DC voltage level.
  • DC voltage level depends on the input voltage and is 1.45 higher then the rms value of the input voltage.
  • a half-controlled thyristor is made of three thyristors 15 and three diodes 16 .
  • Three snubber circuits 17 are connected to the anodes and cathodes of the three thyristors 15 .
  • the RC components have a low power rating due to the small voltage slope transient increase imposed by the half-controlled rectifier compared to the full-controlled version.
  • a soft start is used to initially charge the DC capacitor bank that is connected to the half-controlled thyristor output. The DC capacitor fixed voltage is maintained through the first stage startup.
  • the second mode requires control of the step-up (boost) circuit shown in FIG. 8 .
  • the bus is already charged to a level dependent on the AC input rmns voltage value and the motor is at 80% of the desired speed.
  • the voltage level is changed by changing the switch duty ration, which is refined as the ration of the on duration to the switching time period.
  • the switch control signal which controls the state (on or off) of the switch, is generated by comparing a signal-level control voltage with a repetitive waveform. The frequency of the repetitive waveform with a constant peak, a sawtooth shape, establishes the switching frequency.
  • the voltage controlled IGBT circuit shown in FIG. 7 is in a six-step control mode which obtains the increase of the motor speed to a desired nominal value.
  • Current flows through the two motor phase windings 20 at any time depending on the on/off setting of the IGBT switches.
  • Each of the six IGBT switches in on for 120° and off for 60° and is regulated according to a lookup table.
  • a positive voltage is applied.
  • energizing is stopped.
  • Energizing is then conducted in the same manner in the other two phases.
  • a variable timing of energizing is applied in respective three phases so that there is a difference of 120° between phases. This makes it possible to drive a motor when a magnetic rotation field is generated.
  • a position detecting circuit is based on the Hall effect characteristics. Three Hall sensors are mounted 60° apart and designed to detect the stray magnetic fields from the motor rotor poles. A positive signal voltage is latched when a rotor south pole magnet passes by the sensor; otherwise the signal is zero.
  • the Hall effect pickups enable a closed loop commutation of the inverter and motor stator windings.
  • motor current is optimized by controlling the current phase advance to related induced back EMF (electro-motive force) in the stator winding.
  • a back EMF zero crossing is used as a reference point for the current winding injection.
  • the Hall sensors detect the back EMF zero crossing.
  • the system controller performs all control functions including: motor startup, PWM control, boost control, six step control, motor position detection, current optimization and speed control.
  • the compressor controller controls start and stop functions.
  • a serial link communication is established between the compressor and motor controllers.
  • Motor control setpoints are passed from the compressor controller to the motor controller and they are: desired speed set point, low speed alarm and trip setpoint, high speed alarm and trip setpoint, maximum amperage alarm and trip setpoint, lead angle and low DC bus alarm setpoint.
  • An alarm action is activated when a monitored parameter has reached an unacceptable but not critical level of operation.
  • a trip action is activated when a monitored parameter has reached a critical and unsafe level of operation.
  • the system controller performs all trip functions. Motor/controller analog input readings are passed to the compressor controller for display and they are speed, amperage, DC bus voltage, and motor power.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Permanent Field Magnets Of Synchronous Machinery (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Brushless Motors (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
US10/128,136 2001-04-23 2002-04-23 Multi-stage centrifugal compressor driven by integral high speed motor Expired - Lifetime US6579078B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10/128,136 US6579078B2 (en) 2001-04-23 2002-04-23 Multi-stage centrifugal compressor driven by integral high speed motor

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US28583701P 2001-04-23 2001-04-23
US10/128,136 US6579078B2 (en) 2001-04-23 2002-04-23 Multi-stage centrifugal compressor driven by integral high speed motor

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US20020192089A1 US20020192089A1 (en) 2002-12-19
US6579078B2 true US6579078B2 (en) 2003-06-17

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US (1) US6579078B2 (fr)
EP (1) EP1390618B1 (fr)
JP (2) JP4136667B2 (fr)
KR (1) KR100843500B1 (fr)
CN (1) CN100351516C (fr)
AT (1) ATE511020T1 (fr)
AU (1) AU2002307461A1 (fr)
WO (1) WO2002086324A2 (fr)

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020158102A1 (en) * 2001-04-30 2002-10-31 Patton James Andrew Portable pneumatic tool powered by an onboard compressor
US20030037555A1 (en) * 2000-03-14 2003-02-27 Street Norman E. Distributed intelligence control for commercial refrigeration
US20040005228A1 (en) * 2002-07-02 2004-01-08 R & D Dynamics Corporation Motor driven centrifugal compressor/blower
US20040016253A1 (en) * 2000-03-14 2004-01-29 Hussmann Corporation Refrigeration system and method of operating the same
US20040179947A1 (en) * 2002-12-19 2004-09-16 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor
WO2005080814A1 (fr) * 2004-02-23 2005-09-01 Atlas Copco Airpower, Naamloze Vennootschap Machine a lubrification de palier amelioree
US20050252220A1 (en) * 2000-03-14 2005-11-17 Hussmann Corporation Refrigeration system and method of operating the same
GB2416806A (en) * 2004-07-31 2006-02-08 Fluid Power Design Ltd Compressor arrangement with intercooler and air bearings
US20060032484A1 (en) * 2004-08-11 2006-02-16 Hutchinson Sean G Electro-charger
US20070059186A1 (en) * 2001-04-30 2007-03-15 Black & Decker Inc. Pneumatic compressor
US20070065300A1 (en) * 2005-09-19 2007-03-22 Ingersoll-Rand Company Multi-stage compression system including variable speed motors
US20070189905A1 (en) * 2006-02-13 2007-08-16 Ingersoll-Rand Company Multi-stage compression system and method of operating the same
US20070212232A1 (en) * 2004-06-29 2007-09-13 Johnson Controls Technology Company System and method for cooling a compressor motor
US20080115527A1 (en) * 2006-10-06 2008-05-22 Doty Mark C High capacity chiller compressor
US20080181794A1 (en) * 2007-01-26 2008-07-31 Steinfels Craig R Mobile pneumatic compressor
US7407371B2 (en) * 2003-10-29 2008-08-05 Michele Leone Centrifugal multistage pump
US20080232962A1 (en) * 2007-03-20 2008-09-25 Agrawal Giridhari L Turbomachine and method for assembly thereof using a split housing design
US7442014B1 (en) 2003-10-29 2008-10-28 Paul Craig Mellinger Fluid transfer system and method for transferring fluid
WO2008136796A1 (fr) * 2007-05-07 2008-11-13 Carrier Corporation Appareil d'entraînement de compresseur à moteur
US20090087299A1 (en) * 2007-10-02 2009-04-02 Agrawal Giridhari L Foil gas bearing supported high temperature centrifugal blower and method for cooling thereof
US20090136335A1 (en) * 2005-08-25 2009-05-28 Ntn Corporation Turbine unit for refrigerating/cooling air cycle
US20090205362A1 (en) * 2008-02-20 2009-08-20 Haley Paul F Centrifugal compressor assembly and method
US20090229280A1 (en) * 2008-03-13 2009-09-17 Doty Mark C High capacity chiller compressor
US20090241595A1 (en) * 2008-03-27 2009-10-01 Praxair Technology, Inc. Distillation method and apparatus
US20090241771A1 (en) * 2008-03-27 2009-10-01 Praxair Technology, Inc. Systems and methods for gas separation using high-speed permanent magnet motors with centrifugal compressors
US20100080701A1 (en) * 2008-09-30 2010-04-01 Masahiko Ono Plain bearing unit
WO2011014934A1 (fr) 2009-08-03 2011-02-10 Atlas Copco Airpower Système de turbocompresseur
US7975506B2 (en) 2008-02-20 2011-07-12 Trane International, Inc. Coaxial economizer assembly and method
US20110169273A1 (en) * 2008-09-26 2011-07-14 Arb Greenpower, Llc Hybrid energy conversion system
US8037713B2 (en) 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
US20120051952A1 (en) * 2010-08-28 2012-03-01 Andreas Knoop Charging device for an energy conversion device
US20120087810A1 (en) * 2009-01-30 2012-04-12 Jouko Tapani Peussa Multi-stage centrifugal compressors
DE102011121223A1 (de) * 2011-12-15 2013-06-20 Robert Bosch Gmbh Turboverdichter
US8529665B2 (en) 2010-05-12 2013-09-10 Praxair Technology, Inc. Systems and methods for gas separation using high-speed induction motors with centrifugal compressors
US8657918B2 (en) 2011-11-17 2014-02-25 Praxair Technology, Inc. Cyclic adsorption process using centrifugal machines
US20140105765A1 (en) * 2011-05-31 2014-04-17 Fmc Kongsberg Subsea As Subsea compressor directly driven by a permanent magnet motor with stator and rotor submerged in liquid
US8925197B2 (en) 2012-05-29 2015-01-06 Praxair Technology, Inc. Compressor thrust bearing surge protection
US20150219106A1 (en) * 2012-06-26 2015-08-06 Robert Bosch Gmbh Turbo compressor
US20150244239A1 (en) * 2014-02-21 2015-08-27 Skf Magnetic Mechatronics Modular assembly of motor and magnetic bearings, and method to manufacture such an assembly
US20150308456A1 (en) * 2014-02-19 2015-10-29 Honeywell International Inc. Electric motor-driven compressor having bi-directional liquid coolant passage
US20160033197A1 (en) * 2012-10-03 2016-02-04 Nick J. Degenstein Method for compressing an incoming feed air stream in a cryogenic air separation plant
US20160032931A1 (en) * 2014-07-29 2016-02-04 Hyundai Motor Company Cooling unit of air compressor for fuel cell vehicle
US20160033196A1 (en) * 2012-10-03 2016-02-04 Henry E. Howard Method for compressing an incoming feed air stream in a cryogenic air separation plant
US20160032935A1 (en) * 2012-10-03 2016-02-04 Carl L. Schwarz System and apparatus for compressing and cooling an incoming feed air stream in a cryogenic air separation plant
US9353765B2 (en) 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
US9476428B2 (en) 2011-06-01 2016-10-25 R & D Dynamics Corporation Ultra high pressure turbomachine for waste heat recovery
US9909438B2 (en) 2016-04-12 2018-03-06 United Technologies Corporation Hydrodynamic carbon face seal pressure booster
US9951784B2 (en) 2010-07-27 2018-04-24 R&D Dynamics Corporation Mechanically-coupled turbomachinery configurations and cooling methods for hermetically-sealed high-temperature operation
US10006465B2 (en) 2010-10-01 2018-06-26 R&D Dynamics Corporation Oil-free water vapor blower
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
US20180238347A1 (en) * 2015-09-04 2018-08-23 Turbowin Co., Ltd. Direct drive type dual turbo blower cooling structure
US10072468B2 (en) 2012-12-07 2018-09-11 Trane International Inc. Motor cooling system for chillers
US10280850B1 (en) 2018-01-23 2019-05-07 Ford Global Technologies, Llc Double-ended electric supercharger
US20220106967A1 (en) * 2018-06-25 2022-04-07 Cluster Lng Co., Ltd. Combustible gas compressor

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4010212B2 (ja) * 2002-09-17 2007-11-21 トヨタ自動車株式会社 回転電機潤滑油排出手段を有する過給機
US7160086B2 (en) 2003-01-29 2007-01-09 Sundyne Corporation Rotary machine cooling system
GB0313143D0 (en) * 2003-06-07 2003-07-09 Boc Group Plc Sewage aeration
FR2864214B1 (fr) * 2003-12-22 2017-04-21 Air Liquide Appareil de separation d'air, appareil integre de separation d'air et de production d'un metal et procede de demarrage d'un tel appareil de separation d'air
US7757502B2 (en) * 2004-09-22 2010-07-20 Hamilton Sundstrand Corporation RAM fan system for an aircraft environmental control system
US7811068B2 (en) * 2005-11-16 2010-10-12 General Electric Company Methods and apparatus for transporting natural gas through a pipeline
US9212779B2 (en) * 2010-11-29 2015-12-15 Lincoln Industrial Corporation Pump having diagnostic system
JP5899412B2 (ja) * 2011-12-09 2016-04-06 パナソニックＩｐマネジメント株式会社 回転角度検出装置
DE102011120767A1 (de) 2011-12-10 2013-06-13 Robert Bosch Gmbh Elektrohydraulische Steuereinrichtung
CN103047155B (zh) * 2011-12-29 2015-07-29 摩尔动力(北京)技术股份有限公司 工质隔离涡轮压气机
CN102619769A (zh) * 2012-04-17 2012-08-01 江苏乘帆压缩机有限公司 高压离心风机
US20130334911A1 (en) * 2012-06-13 2013-12-19 Remy Technologies, L.L.C. Electric motor including a positive pressure introduction system and method
WO2014151375A1 (fr) * 2013-03-15 2014-09-25 Trane International Inc. Appareils, systèmes et procédés de fonctionnement et de commande d'entraînement à fréquence variable
CN104564737A (zh) * 2014-01-13 2015-04-29 陈永刚 一种旋轮增压制冷压缩机
CN104009579B (zh) * 2014-06-12 2017-02-01 麦科威（昆山）机械有限公司 塑料高速混合机电机轴支撑结构
JP6428434B2 (ja) * 2015-03-27 2018-11-28 株式会社豊田自動織機 圧縮機
CN104879306B (zh) * 2015-05-13 2017-03-08 苏州市朗吉科技有限公司 一种离心压缩机
CN105114341B (zh) * 2015-09-01 2017-11-10 广东美芝制冷设备有限公司 离心压缩机及具有其的房间空调器
CN106015032B (zh) * 2016-06-28 2018-05-22 杭州万辰机电科技有限公司 离心压缩机
US10724546B2 (en) * 2016-08-05 2020-07-28 Daikin Applied Americas Inc. Centrifugal compressor having a casing with an adjustable clearance and connections for a variable flow rate cooling medium, impeller clearance control apparatus for centrifugal compressor, and impeller clearance control method for centrifugal compressor
JP2018123797A (ja) * 2017-02-02 2018-08-09 トヨタ自動車株式会社 エア供給システム
EP3786459B1 (fr) * 2018-11-15 2023-08-16 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Compresseur centrifuge et turbocompresseur comportant ledit compresseur centrifuge
CN110397607A (zh) * 2019-07-09 2019-11-01 中国航发哈尔滨东安发动机有限公司 一种高速直驱式双吸离心蒸汽压缩机
US11387712B2 (en) * 2019-09-13 2022-07-12 GM Global Technology Operations LLC Method to reduce oil shear drag in airgap
CN111503009B (zh) * 2020-04-24 2021-07-20 浙江浙水工贸有限公司 一种高扬程屏蔽式永磁多级泵及其控制方法
CN112761973A (zh) * 2021-01-08 2021-05-07 西安交通大学 一种超高速永磁电机驱动的氮气压缩机结构
CN117927439A (zh) * 2024-03-18 2024-04-26 潍柴动力股份有限公司 一种一体式电动泵及车辆

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951573A (en) * 1946-07-16 1976-04-20 The United States Of America As Represented By The United States Energy Research And Development Administration Fluid lubricated bearing construction
US4125345A (en) * 1974-09-20 1978-11-14 Hitachi, Ltd. Turbo-fluid device
US4734018A (en) * 1985-12-27 1988-03-29 Hitachi, Ltd. Vacuum pump with plural labyrinth seal portions
US5638796A (en) * 1994-06-03 1997-06-17 Adams, Iii; Herbert L. Electric supercharger
US5801470A (en) 1996-12-19 1998-09-01 General Electric Company Rotors with retaining cylinders and reduced harmonic field effect losses
US5857348A (en) * 1993-06-15 1999-01-12 Multistack International Limited Compressor
US5957667A (en) * 1997-05-23 1999-09-28 Ballard Generation Systems Inc. Oilless compressor with a pressurizable crankcase and motor containment vessel
WO2000017524A1 (fr) 1998-09-18 2000-03-30 Hitachi, Ltd. Compresseur centrifuge a deux allures commande directement par un moteur

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4616483A (en) * 1985-04-29 1986-10-14 Carrier Corporation Diffuser wall control
JPH02130286A (ja) * 1988-11-08 1990-05-18 Diesel Kiki Co Ltd 空気調和機
JPH05502076A (ja) * 1989-12-20 1993-04-15 アライド・シグナル・インコーポレーテツド 可変速ターボ真空ポンプ
JPH05207688A (ja) * 1992-01-27 1993-08-13 Hitachi Ltd 電動機の回転子
US5350039A (en) * 1993-02-25 1994-09-27 Nartron Corporation Low capacity centrifugal refrigeration compressor
KR100189150B1 (ko) * 1997-02-26 1999-06-01 윤종용 공기조화기용 원심압축기
US6102672A (en) * 1997-09-10 2000-08-15 Turbodyne Systems, Inc. Motor-driven centrifugal air compressor with internal cooling airflow
JP3484051B2 (ja) * 1997-09-10 2004-01-06 株式会社 日立インダストリイズ 永久磁石式同期電動機及びその製造方法ならびに永久磁石式同期電動機を備えた遠心圧縮機
JP3889532B2 (ja) * 1998-09-07 2007-03-07 三菱電機株式会社 Ｄｃブラシレスモータの組込着磁方法

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951573A (en) * 1946-07-16 1976-04-20 The United States Of America As Represented By The United States Energy Research And Development Administration Fluid lubricated bearing construction
US4125345A (en) * 1974-09-20 1978-11-14 Hitachi, Ltd. Turbo-fluid device
US4734018A (en) * 1985-12-27 1988-03-29 Hitachi, Ltd. Vacuum pump with plural labyrinth seal portions
US5857348A (en) * 1993-06-15 1999-01-12 Multistack International Limited Compressor
US5638796A (en) * 1994-06-03 1997-06-17 Adams, Iii; Herbert L. Electric supercharger
US5801470A (en) 1996-12-19 1998-09-01 General Electric Company Rotors with retaining cylinders and reduced harmonic field effect losses
US5957667A (en) * 1997-05-23 1999-09-28 Ballard Generation Systems Inc. Oilless compressor with a pressurizable crankcase and motor containment vessel
WO2000017524A1 (fr) 1998-09-18 2000-03-30 Hitachi, Ltd. Compresseur centrifuge a deux allures commande directement par un moteur

Cited By (95)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
US20030037555A1 (en) * 2000-03-14 2003-02-27 Street Norman E. Distributed intelligence control for commercial refrigeration
US20040016253A1 (en) * 2000-03-14 2004-01-29 Hussmann Corporation Refrigeration system and method of operating the same
US8850838B2 (en) 2000-03-14 2014-10-07 Hussmann Corporation Distributed intelligence control for commercial refrigeration
US20050252220A1 (en) * 2000-03-14 2005-11-17 Hussmann Corporation Refrigeration system and method of operating the same
US7320225B2 (en) * 2000-03-14 2008-01-22 Hussmann Corporation Refrigeration system and method of operating the same
US20070059186A1 (en) * 2001-04-30 2007-03-15 Black & Decker Inc. Pneumatic compressor
US20020158102A1 (en) * 2001-04-30 2002-10-31 Patton James Andrew Portable pneumatic tool powered by an onboard compressor
US7494035B2 (en) 2001-04-30 2009-02-24 Black & Decker Inc. Pneumatic compressor
US7225959B2 (en) 2001-04-30 2007-06-05 Black & Decker, Inc. Portable, battery-powered air compressor for a pneumatic tool system
US20040005228A1 (en) * 2002-07-02 2004-01-08 R & D Dynamics Corporation Motor driven centrifugal compressor/blower
US7063519B2 (en) 2002-07-02 2006-06-20 R & D Dynamics Corporation Motor driven centrifugal compressor/blower
US6997686B2 (en) 2002-12-19 2006-02-14 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor
US20040179947A1 (en) * 2002-12-19 2004-09-16 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor
US7407371B2 (en) * 2003-10-29 2008-08-05 Michele Leone Centrifugal multistage pump
US7442014B1 (en) 2003-10-29 2008-10-28 Paul Craig Mellinger Fluid transfer system and method for transferring fluid
BE1015913A3 (nl) 2004-02-23 2005-11-08 Atlas Copco Airpower Nv Machine met verbeterde lagersmering.
CN1942684B (zh) * 2004-02-23 2011-01-05 艾拉斯科普库空气动力股份有限公司 具有改进轴承润滑的机器
US20070177835A1 (en) * 2004-02-23 2007-08-02 Verhaegen Ken G H Machine with an improved bearing lubrication
US7594757B2 (en) 2004-02-23 2009-09-29 Atlas Copco Airpower, Naamloze Vennootschap Machine with an improved bearing lubrication
WO2005080814A1 (fr) * 2004-02-23 2005-09-01 Atlas Copco Airpower, Naamloze Vennootschap Machine a lubrification de palier amelioree
US8021127B2 (en) * 2004-06-29 2011-09-20 Johnson Controls Technology Company System and method for cooling a compressor motor
US20110300006A1 (en) * 2004-06-29 2011-12-08 Johnson Controls Technology Company System and method for cooling a compressor motor
US20070212232A1 (en) * 2004-06-29 2007-09-13 Johnson Controls Technology Company System and method for cooling a compressor motor
US8465265B2 (en) * 2004-06-29 2013-06-18 Johnson Controls Technology Company System and method for cooling a compressor motor
GB2416806A (en) * 2004-07-31 2006-02-08 Fluid Power Design Ltd Compressor arrangement with intercooler and air bearings
US20060032484A1 (en) * 2004-08-11 2006-02-16 Hutchinson Sean G Electro-charger
US20090136335A1 (en) * 2005-08-25 2009-05-28 Ntn Corporation Turbine unit for refrigerating/cooling air cycle
US8215898B2 (en) * 2005-08-25 2012-07-10 Ntn Corporation Turbine unit for refrigerating/cooling air cycle
US20070065300A1 (en) * 2005-09-19 2007-03-22 Ingersoll-Rand Company Multi-stage compression system including variable speed motors
WO2007095537A1 (fr) * 2006-02-13 2007-08-23 Ingersoll-Rand Company Systeme de compression a plusieurs etages et son procede d'actionnement
US20070189905A1 (en) * 2006-02-13 2007-08-16 Ingersoll-Rand Company Multi-stage compression system and method of operating the same
CN101421519B (zh) * 2006-02-13 2012-07-04 英格索尔-兰德公司 多级压缩系统和操作该多级压缩系统的方法
US20080115527A1 (en) * 2006-10-06 2008-05-22 Doty Mark C High capacity chiller compressor
US8156757B2 (en) 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US20080181794A1 (en) * 2007-01-26 2008-07-31 Steinfels Craig R Mobile pneumatic compressor
US20080232962A1 (en) * 2007-03-20 2008-09-25 Agrawal Giridhari L Turbomachine and method for assembly thereof using a split housing design
US20100139298A1 (en) * 2007-05-07 2010-06-10 Alexander Lifson Motor-compressor drive apparatus
WO2008136796A1 (fr) * 2007-05-07 2008-11-13 Carrier Corporation Appareil d'entraînement de compresseur à moteur
US20090087299A1 (en) * 2007-10-02 2009-04-02 Agrawal Giridhari L Foil gas bearing supported high temperature centrifugal blower and method for cooling thereof
US8215928B2 (en) 2007-10-02 2012-07-10 R&D Dynamics Corporation Foil gas bearing supported high temperature centrifugal blower and method for cooling thereof
US8627680B2 (en) 2008-02-20 2014-01-14 Trane International, Inc. Centrifugal compressor assembly and method
US7856834B2 (en) 2008-02-20 2010-12-28 Trane International Inc. Centrifugal compressor assembly and method
US8037713B2 (en) 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
US7975506B2 (en) 2008-02-20 2011-07-12 Trane International, Inc. Coaxial economizer assembly and method
US9683758B2 (en) 2008-02-20 2017-06-20 Trane International Inc. Coaxial economizer assembly and method
US9353765B2 (en) 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
US9556875B2 (en) 2008-02-20 2017-01-31 Trane International Inc. Centrifugal compressor assembly and method
US20090205362A1 (en) * 2008-02-20 2009-08-20 Haley Paul F Centrifugal compressor assembly and method
US8397534B2 (en) 2008-03-13 2013-03-19 Aff-Mcquay Inc. High capacity chiller compressor
US20090229280A1 (en) * 2008-03-13 2009-09-17 Doty Mark C High capacity chiller compressor
US7785405B2 (en) 2008-03-27 2010-08-31 Praxair Technology, Inc. Systems and methods for gas separation using high-speed permanent magnet motors with centrifugal compressors
US20090241595A1 (en) * 2008-03-27 2009-10-01 Praxair Technology, Inc. Distillation method and apparatus
US20090241771A1 (en) * 2008-03-27 2009-10-01 Praxair Technology, Inc. Systems and methods for gas separation using high-speed permanent magnet motors with centrifugal compressors
US20110169273A1 (en) * 2008-09-26 2011-07-14 Arb Greenpower, Llc Hybrid energy conversion system
US20100080701A1 (en) * 2008-09-30 2010-04-01 Masahiko Ono Plain bearing unit
US20120087810A1 (en) * 2009-01-30 2012-04-12 Jouko Tapani Peussa Multi-stage centrifugal compressors
AU2009338633B2 (en) * 2009-01-30 2014-04-24 Gardner Denver Deutschland Gmbh Improvements in multi-stage centrifugal compressors
AU2009338633C1 (en) * 2009-01-30 2014-08-21 Gardner Denver Deutschland Gmbh Improvements in multi-stage centrifugal compressors
US9109603B2 (en) * 2009-01-30 2015-08-18 Gardner Denver Deutschland Gmbh Multi-stage centrifugal compressors
US9470238B2 (en) 2009-08-03 2016-10-18 Atlas Copco Airpower, Naamloze Vennootschap Electric motor having segmented stator windings
WO2011014934A1 (fr) 2009-08-03 2011-02-10 Atlas Copco Airpower Système de turbocompresseur
US8529665B2 (en) 2010-05-12 2013-09-10 Praxair Technology, Inc. Systems and methods for gas separation using high-speed induction motors with centrifugal compressors
US9951784B2 (en) 2010-07-27 2018-04-24 R&D Dynamics Corporation Mechanically-coupled turbomachinery configurations and cooling methods for hermetically-sealed high-temperature operation
US20120051952A1 (en) * 2010-08-28 2012-03-01 Andreas Knoop Charging device for an energy conversion device
US10006465B2 (en) 2010-10-01 2018-06-26 R&D Dynamics Corporation Oil-free water vapor blower
US10794386B2 (en) * 2011-05-31 2020-10-06 Fmc Kongsberg Subsea As Subsea compressor directly driven by a permanent magnet motor with stator and rotor submerged in liquid
US20140105765A1 (en) * 2011-05-31 2014-04-17 Fmc Kongsberg Subsea As Subsea compressor directly driven by a permanent magnet motor with stator and rotor submerged in liquid
US9476428B2 (en) 2011-06-01 2016-10-25 R & D Dynamics Corporation Ultra high pressure turbomachine for waste heat recovery
US8657918B2 (en) 2011-11-17 2014-02-25 Praxair Technology, Inc. Cyclic adsorption process using centrifugal machines
US8728215B2 (en) 2011-11-17 2014-05-20 Praxair Technology, Inc. Cyclic adsorption process using centrifugal machines
DE102011121223A1 (de) * 2011-12-15 2013-06-20 Robert Bosch Gmbh Turboverdichter
US8925197B2 (en) 2012-05-29 2015-01-06 Praxair Technology, Inc. Compressor thrust bearing surge protection
US20150219106A1 (en) * 2012-06-26 2015-08-06 Robert Bosch Gmbh Turbo compressor
US20160032935A1 (en) * 2012-10-03 2016-02-04 Carl L. Schwarz System and apparatus for compressing and cooling an incoming feed air stream in a cryogenic air separation plant
US20160033196A1 (en) * 2012-10-03 2016-02-04 Henry E. Howard Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10533565B2 (en) 2012-10-03 2020-01-14 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10519962B2 (en) 2012-10-03 2019-12-31 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10533564B2 (en) 2012-10-03 2020-01-14 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US20160033197A1 (en) * 2012-10-03 2016-02-04 Nick J. Degenstein Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10443603B2 (en) * 2012-10-03 2019-10-15 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10385861B2 (en) * 2012-10-03 2019-08-20 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10072468B2 (en) 2012-12-07 2018-09-11 Trane International Inc. Motor cooling system for chillers
US20150308456A1 (en) * 2014-02-19 2015-10-29 Honeywell International Inc. Electric motor-driven compressor having bi-directional liquid coolant passage
US10033246B2 (en) * 2014-02-21 2018-07-24 Skf Magnetic Mechatronics Modular assembly of motor and magnetic bearings, and method to manufacture such an assembly
US20150244239A1 (en) * 2014-02-21 2015-08-27 Skf Magnetic Mechatronics Modular assembly of motor and magnetic bearings, and method to manufacture such an assembly
US9863430B2 (en) * 2014-07-29 2018-01-09 Hyundai Motor Company Cooling unit of air compressor for fuel cell vehicle
US20160032931A1 (en) * 2014-07-29 2016-02-04 Hyundai Motor Company Cooling unit of air compressor for fuel cell vehicle
US20180238347A1 (en) * 2015-09-04 2018-08-23 Turbowin Co., Ltd. Direct drive type dual turbo blower cooling structure
US10753372B2 (en) * 2015-09-04 2020-08-25 Turbowin Co., Ltd. Direct drive type dual turbo blower cooling structure
US9909438B2 (en) 2016-04-12 2018-03-06 United Technologies Corporation Hydrodynamic carbon face seal pressure booster
US10280850B1 (en) 2018-01-23 2019-05-07 Ford Global Technologies, Llc Double-ended electric supercharger
US20220106967A1 (en) * 2018-06-25 2022-04-07 Cluster Lng Co., Ltd. Combustible gas compressor
US11815103B2 (en) * 2018-06-25 2023-11-14 Cluster Lng Co., Ltd. Boil-off gas compressor for LNG fueled ship
US11892010B2 (en) * 2018-06-25 2024-02-06 Cluster Lng Co., Ltd. Combustible gas compressor

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ATE511020T1 (de) 2011-06-15
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AU2002307461A1 (en) 2002-11-05
US20020192089A1 (en) 2002-12-19
CN100351516C (zh) 2007-11-28
EP1390618A4 (fr) 2009-06-17
WO2002086324A2 (fr) 2002-10-31
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